US8079331B2 - Internal-combustion engine, in particular a two-cylinder engine, provided with a simplified system for variable actuation of the engine valves - Google Patents

Internal-combustion engine, in particular a two-cylinder engine, provided with a simplified system for variable actuation of the engine valves Download PDF

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US8079331B2
US8079331B2 US12/434,922 US43492209A US8079331B2 US 8079331 B2 US8079331 B2 US 8079331B2 US 43492209 A US43492209 A US 43492209A US 8079331 B2 US8079331 B2 US 8079331B2
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engine
pressurized
valves
fluid
intake
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US20090320776A1 (en
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Francesco Vattaneo
Laura Gianolio
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Centro Ricerche Fiat SCpA
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Centro Ricerche Fiat SCpA
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Assigned to C.R.F. SOCIETA CONSORTILE PER AZIONI reassignment C.R.F. SOCIETA CONSORTILE PER AZIONI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GIANOLIO, LAURA, VATTANEO, FRANCESCO
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the present invention relates to multi-cylinder internal-combustion engines, particularly for motor vehicles, of the type comprising:
  • each intake valve is controlled by the respective tappet, against the action of the aforesaid elastic return means, by interposition of hydraulic means including a pressurized-fluid chamber;
  • said pressurized-fluid chamber being designed to be connected by means of a solenoid valve to an exhaust channel in order to uncouple the intake valve of the respective tappet and cause fast closing of the valve as a result of the respective elastic return means;
  • the object of the present invention is to improve the aforesaid system by proposing a version thereof that is substantially simplified as compared to the known embodiments.
  • the subject of the invention is an engine of the type indicated at the start of the present description, characterized in that:
  • the idea underlying the present invention consequently consists in controlling by means of a single solenoid valve variable actuation of the intake valves of two (or more) different engine cylinders, exploiting the fact that in the engine according to the invention the intake strokes of the two different cylinders are sufficiently distant to enable use of one and the same solenoid valve for controlling the intake valves of both of the cylinders.
  • One and the same solenoid valve consequently controls in a pre-set way opening and closing of both the intake valve (or valves) of a first cylinder of the engine, when this is in its intake stroke, and the intake valve (or valves) of a second cylinder of the engine, when this is in its intake stroke.
  • the typical case of engine to which the invention is particularly aimed is that of a compact two-cylinder engine for a motor vehicle of small dimensions, in which the two cranks of the crankshaft associated to the two pistons of the engine are out of phase with respect to one another by 0° (or, what amounts to the same thing, by 360°) so that the two pistons associated to said cylinders reach the Top Dead Centre (TDC) and the Bottom Dead Centre (BDC) simultaneously in the various steps of operation of the engine.
  • TDC Top Dead Centre
  • BDC Bottom Dead Centre
  • the intake strokes of the two cylinders are out of phase with respect to one another by one complete revolution of the engine shaft.
  • the engine is of the type, in itself known (see, for example, EP 1 555 398 B1), provided in which is a main channel for supply of fluid under pressure communicating with the pressurized chambers, which are associated to the intake valves of the various cylinders via respective first non-return valves, which enable the passage of fluid only in the direction of the pressurized-fluid chambers.
  • the invention is moreover characterized in that the pressurized chambers, which are associated to the intake valves of the two aforesaid different engine cylinders are also directly connected to one another by a by-pass channel, via two respective second non-return valves that enable the passage of fluid only from each of the two pressurized chambers towards said by-pass channel, said by-pass channel being designed to be set in communication via the aforesaid single common solenoid valve with a common exhaust channel for the two pressurized chambers, which are associated to the intake valves of the two cylinders.
  • a single common fluid accumulator associated to the two aforesaid pressurized chambers, which are associated to the intake valves of said two different engine cylinders, is a single common fluid accumulator, which is in communication with said common exhaust channel.
  • the main channel ( 50 ) for supply of pressurized fluid there is preferably interposed, in a way in itself known (see EP 1 555 398 B1), at least one fluid tank ( 40 ), vented at the top to the atmosphere, having an inlet ( 40 a ) at its top for receiving the pressurized fluid and an outlet ( 40 b ) on its bottom connected to the pressurized chambers (C) via said first non-return valves (V 1 ), which is designed to perform a siphon function for purging the air present in the fluid.
  • the engine according to the invention is moreover characterized in that said tank has a further outlet on its bottom communicating with said common exhaust channel.
  • the engine according to the invention enables a substantial simplification and reduction of components as compared to the engines of the known type referred to at the start of the present description.
  • the system of variable actuation of the intake valves associated to the various engine cylinders enables a substantial reduction (specifically halving) of the number of solenoid valves designed for control, as well as a reduction (typically halving) of the number of fluid accumulators associated to the pressurized chambers for actuation of the valves of the various cylinders.
  • a further reduction regards also the number of fluid tanks with which the system is provided.
  • the system according to the invention guarantees a better cold filling of the pressurized-fluid chambers thanks to the pre-arrangement of the aforesaid non-return valves that enable a larger area of passage as compared to that of the solenoid valves used in the known solutions.
  • the reduction of the components leads also to a smaller encumbrance of the entire system, a simplification of the controls that must be pre-arranged in the electronic control unit, and a simplification of the wiring of the solenoid valves.
  • FIG. 1 is a cross-sectional view of an engine according to the known art, of the type described for example in EP 1 555 398 B1 filed in the name of the present applicant, where said engine is presented as known in turn from EP 0 803 642 B1, likewise filed in the name of the present applicant;
  • FIG. 2A is a schematic perspective view of the engine shaft and of the two pistons of a compact two-cylinder engine, with cranks out of phase by 360°, according to the present invention
  • FIG. 2B illustrates a diagram that shows the lifts of the intake and exhaust valves of the engine represented in FIG. 2A ;
  • FIG. 3 is a schematic view of a system for variable actuation of the valves of an engine according to the known art.
  • FIG. 4 is a schematic view of a system for variable actuation of the valves of an engine according to the invention.
  • FIG. 1 of the present document coincides with FIG. 1 of the European patent EP 0 803 642 B1 filed in the name of the present applicant. It illustrates a multi-cylinder engine, for example, an engine with four cylinders in line, comprising a cylinder head 1 .
  • the cylinder head 1 comprises, for each cylinder, a cavity 2 formed by the base surface 3 of the cylinder head 1 , defining the combustion chamber, giving out into which are two intake pipes 4 , 5 and two exhaust pipes 6 . Communication of the two intake pipes 4 , 5 with the combustion chamber 2 is controlled by two intake valves 7 , of the traditional mushroom type, each comprising a stem 8 mounted slidable in the body of the cylinder head 1 .
  • Each valve 7 is recalled towards the position of closing by springs 9 set between an internal surface of the cylinder head 1 and an end cup 10 of the valve. Communication of the two exhaust pipes 6 with the combustion chamber is controlled by two valves 70 , which are also of a traditional type, associated to which are springs 9 for return towards the closed position. Opening of each intake valve 7 is controlled, in the way that will be described in what follows, by a camshaft 11 mounted so that it can rotate about an axis 12 within supports of the cylinder head 1 , and comprising a plurality of cams 14 for actuation of the intake valves 7 .
  • Each cam 14 co-operates with the cap 15 of a tappet 16 slidably mounted along an axis 17 , which, in the case of the example illustrated in the prior document cited, is directed substantially at 90° with respect to the axis of the valve 7 .
  • the cap 15 is recalled against the cam 14 by a spring associated thereto.
  • the tappet 16 constitutes a pumping piston mounted slidable within a bushing 18 carried by a body 19 of a pre-assembly 20 , which incorporates all the electrical and hydraulic devices associated to actuation of the intake valves.
  • the pumping piston 16 is able to transmit a thrust to the stem 8 of the valve 7 so as to cause opening of the latter against the action of the elastic means 9 , by means of pressurized fluid (typically oil coming from the circuit for lubrication of the engine) present in a pressure chamber C which the pumping piston 16 faces, and by means of a piston 21 mounted slidable in a cylindrical body constituted by a bushing 22 that is also carried by the body 19 of the subassembly 20 .
  • pressurized-fluid chamber C associated to the intake valve (or valves) 7 of each cylinder can be set in communication with an exhaust channel 23 via a solenoid valve 24 .
  • the solenoid valve 24 which can be of any known type suitable for the function illustrated herein, is controlled by electronic control means, designated schematically by 25 , as a function of signals S indicating parameters of operation of the engine, such as the position of the accelerator and the number of turns of the engine.
  • the solenoid valve is of a normally open type, designed to close following upon a supply of its solenoid.
  • the solenoid valve 24 When the solenoid valve 24 is opened, the chamber C enters into communication with the channel 23 so that the pressurized fluid present in the chamber C flows in said channel, and an uncoupling is obtained of the cam 14 and of the respective tappet 16 from the intake valve 7 , which hence rapidly returns into its closing position under the action of the return springs 9 .
  • By controlling the communication between the chamber C and the exhaust channel 23 it is consequently possible to vary the time and stroke of opening of each intake valve 7 as required.
  • the exhaust channels 23 of the various solenoid valves 24 all give out into one and the same longitudinal channel 26 , which communicates with pressure accumulators 27 , only one of which is visible in FIG. 1 .
  • All the tappets 16 with the associated bushing 18 , the pistons 21 with the associated bushing 22 , the solenoid valves 24 and the corresponding channels 23 , 26 are carried by and made out of the aforesaid body 19 of the pre-assembly 20 to the advantage of rapidity and ease of assembly of the engine.
  • the exhaust valves 70 associated to each cylinder are controlled, in the embodiment illustrated in FIG. 1 , in a traditional way, by a respective camshaft 28 , via respective tappets 29 , even though in principle there is not ruled out, in the case of the prior document cited, an application of the hydraulic-actuation system also to control of the exhaust valve.
  • variable-volume chamber defined within the bushing 22 faces the piston 21 (in FIG. 1 said chamber is illustrated in its condition of minimum volume given that the piston 21 is in its top end-of-travel position) and communicates with the pressurized-fluid chamber C via an opening 30 made in an end wall of the bushing 22 .
  • Said opening 30 is engaged by an end nose 31 of the piston 21 in such a way as to provide a hydraulic braking of the movement of the valve 7 in the closing stage, when the valve is close to the closing position, in so far as the oil present in the variable-volume chamber is forced to flow into the pressurized-fluid chamber C passing through the clearance between the end nose 31 and the wall of the opening 30 engaged thereby.
  • the pressurized-fluid chamber C and the variable-volume chamber of the piston 21 communicate with one another via internal passages made in the body of the piston 21 and controlled by a non-return valve 32 that enables passage of fluid only from the pressurized chamber C to the variable-volume chamber of the piston 21 .
  • the solenoid valve 24 excludes the communication of the pressurized-fluid chamber C with the exhaust channel 23 , the oil present in said chamber transmits the movement of the pumping piston 16 , imparted by the cam 14 , to the piston 21 that controls opening of the valve 7 .
  • the fluid coming from the chamber C reaches the variable-volume chamber of the piston 21 passing through the non-return valve 32 and further passages that set in communication the internal cavity of the piston 21 , which has a tubular conformation, with the variable-volume chamber.
  • the nose 31 comes out of the opening 30 so that the fluid coming from the chamber C can pass directly into the variable-volume chamber through the opening 30 , which is now free.
  • the present invention stems from a particularly simple and efficient version of the system for variable actuation of the valves in association with an internal-combustion engine of the type comprising at least two cylinders that have their respective intake strokes out of phase with respect to one another substantially by one complete revolution of the engine shaft.
  • the typical case which regards particularly (but not exclusively) the present invention is that of a two-cylinder engine in which the cranks associated to the two pistons of the engine are out of phase with respect to one another by 0° (or, what amounts to the same thing, by 360°) of rotation of the engine shaft, according to what is schematically illustrated in FIG. 2A .
  • the reference SH designates as a whole the engine shaft of an internal-combustion engine with two cylinders in line associated to which are two pistons P 1 , P 2 .
  • the shaft SH is carried in rotation about an axis SHA and has cranks CR 1 , CR 2 , out of phase with respect to one another by 0° of rotation of the engine shaft, connected to which are the connecting rods R 1 , R 2 associated to the two pistons P 1 and P 2 slidably mounted in the two cylinders.
  • the arrangement is such that the two pistons P 1 and P 2 reach simultaneously the top dead centre (TDC).
  • FIG. 2B is a schematic illustration of the diagram of the lifts of the intake and exhaust valves associated to the two cylinders C 1 , C 2 , during rotation of the engine shaft.
  • the two-cylinder engine described herein envisages two intake valves for each cylinder.
  • the lines A 1 and A 2 indicate, respectively, the displacement of the intake valves associated to the first cylinder and to the second cylinder during rotation of the engine shaft, whilst the lines S 1 and S 2 indicate the displacement of the exhaust valves associated to the first and second cylinders during rotation of the engine shaft.
  • the spark symbols designated by X 1 and X 2 indicate the instants of ignition of the first and second cylinders.
  • the intake strokes in the first and second cylinders are set at a distance apart from one another by one complete revolution of the engine shaft, a fact that is advantageously exploited in the case of the present invention in the way that will be described in detail in what follows.
  • FIG. 3 is a schematic illustration of the variable-actuation system already proposed by the present applicant in the prior patents, as appears if applied to a two-cylinder engine.
  • the system envisages for each cylinder a pair of intake valves 7 (but the solution can be equally adopted in the case where each cylinder is provided with a single intake valve), each of which is actuated, by means of a hydraulic cylinder 22 of a type similar to what is described above with reference to FIG. 1 , by pressurized oil that arrives from a pressurized chamber C associated to each cylinder.
  • the fluid in the pressurized chamber C is pumped by the pumping piston 16 controlled by the cam.
  • each tappet 15 , 16 is actuated by a respective cam 14 a , 14 b of the camshaft 11 by means of a rocker 35 , having an end 35 a supported in an articulated way, by means of a suspension 35 b , by the structure of the engine cylinder head.
  • the rocker 35 carries in its intermediate area a wheel 35 c , which co-operates with the cam 14 and has its end 35 d opposite to the end 35 a that co-operates with the tappet 15 .
  • cams 14 a , 14 b have been illustrated in the plane of the sheet.
  • a single camshaft 11 is provided (illustrated schematically by a dashed-and-dotted line) mounted on which are both of the cams 14 a , 14 b.
  • a solenoid valve 24 that sets the pressurized chamber C of the respective cylinder in communication with an exhaust channel 23 , connected to which is an accumulator of pressurized fluid 27 designed to receive inside it pressurized fluid with consequent displacement of a piston 27 a against the action of a spring 27 b , and a fluid tank 36 closed at the top by a lid having a hole 37 for communication with the atmosphere (more precisely with the compartment present underneath the lid of the cylinder head), for venting the air possibly present in the oil (see EP 1 243 761 B1 and EP 1 555 398 B1).
  • the pressurized-fluid chambers C are designed to receive pressurized oil from the lubrication circuit of the engine, via a supply pump 38 , which feeds pressurized oil from a tank 39 to the channel 23 , which is connected to the pressurized chambers C via a main fluid tank 40 closed at the top by a lid provided with an opening for venting to the atmosphere 41 .
  • the tank 40 also performs the function of siphon in so far as it receives the fluid from the pump 38 through an inlet 40 a located in its top area and sends fluid to the channel 23 through an outlet 40 b situated in its bottom area so as to enable bleeding of the air present in the oil.
  • Interposed in the communication of the outlet 40 b of the main fluid tank 40 with the two channels 23 that lead to the pressurized chambers C are non-return valves V 1 , which enable the passage of fluid only in the direction of the pressurized chambers C.
  • the solenoid valves 24 are normally open. In said condition, the rotation of the camshaft 11 does not cause actuation of the valves 7 in so far as the latter are withheld in their closed position by the respective return springs, whilst the pressurized oil present in the chambers C is pushed by the pumping pistons 16 into the accumulators 27 given that it cannot pass beyond the non-return valves V 1 .
  • the solenoid valves 24 are actuated by supply of their solenoid, the communication between the pressurized chambers C and the exhaust channels 23 is interrupted so that the movement of the pumping pistons 16 caused by the rotation of the camshaft 11 determines the movement of the intake valves 7 by means of the hydraulic cylinders 22 .
  • control of the solenoid valves is performed so as to vary as required both the instants of opening and of closing of each intake valve and the degree of the lift itself as a function of the operating conditions of the engine in order to obtain the best results, in every operating condition, from the standpoint of the maximum efficiency and/or of the minimum consumption of fuel and/or of the minimum emission of noxious exhaust gases.
  • FIG. 4 illustrates the simplified system for variable actuation of the valves, which is proposed in compliance with the present invention in association with a two-cylinder engine of the type illustrated in FIG. 2A .
  • FIG. 4 the parts in common with the ones of FIG. 3 are designated by the same references. Also in FIG. 4 , for convenience of representation, the camshaft 11 that carries both of the cams 14 a , 14 b is illustrated schematically.
  • the main difference of the system of FIG. 4 with respect to that of FIG. 3 lies in the fact that in said system the communication of the pressurized chambers C associated to the intake valves of the two engine cylinders with the exhaust channel 23 is controlled by a single solenoid valve 24 , said exhaust channel 23 being common for the two pressurized chambers C.
  • a main channel is provided for supply of the pressurized oil, as in the case of the known solution, which receives the oil from the pump 38 and feeds it into the top area of a main tank 40 provided with a top venting hole 41 functioning as siphon, in a way similar to what is illustrated above.
  • the pressurized oil supplied by the pump 38 can be sent from the tank 40 to the pressurized chambers C via two different outlets 40 b made in the bottom area of the tank 40 (to obtain the siphon function), and via two channels interposed in which are the first non-return valves V 1 , having a function similar to the valves V 1 of FIG. 3 , i.e., such as to enable passage of fluid only in the direction of the chambers C.
  • the two pressurized chambers C communicate also directly with one another through a by-pass channel 44 via two non-return valves 72 , which enable the passage of fluid only from the pressurized chambers C to the by-pass channel 44 .
  • the single common solenoid valve 24 controls the communication between said by-pass channel 44 and a common exhaust channel 23 , which is connected to the bottom of the main fluid tank 40 as well as to a single fluid accumulator 27 .
  • the solenoid valve 24 is normally open but is designed to receive a current pulse I 1 , the form of which can be, for example, the one illustrated in FIG. 2B , corresponding to the intake stroke of the first cylinder, and a current pulse I 2 corresponding of to the intake stroke of the second cylinder.
  • a current pulse I 1 the form of which can be, for example, the one illustrated in FIG. 2B
  • I 2 a current pulse corresponding of to the intake stroke of the second cylinder.
  • the system would likewise enable a normally closed solenoid valve given the presence of the non-return valves V 1 that enable supply of the chambers C (topping-up of any oil that has leaked).
  • the system thus enables considerable simplification of the structure and number of components of the assembly for actuation of the valves, leaving, however, unaltered the advantages of the system in terms of overall flexibility as regards to the possibility of varying the time and stroke of opening of the intake valves of each cylinder in the various operating conditions of the engine.
  • the system enables reduction (halving in the specific case described herein) of the number of the solenoid valves (a single solenoid valve instead of two), reduction in the number of the accumulators (a single accumulator instead of two), and reduction in the number of tanks.
  • the arrangement of the system according to the invention guarantees also a better filling in cold conditions of the pressurized chambers C thanks to the presence of the non-return valves that enable a larger area of passage as compared to that of the solenoid valves used in the known solutions.
  • the reduction in the number of elements also leads to a considerable reduction in the overall dimensions of the system for variable actuation of the valves, and a reduction in the number of controls that must be prearranged in the electronic control unit 25 .
  • the wiring is simplified, thanks to the provision of a single solenoid valve. All the aforesaid advantages are particularly important in the case of a compact engine for a motor vehicle of small dimensions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US12/434,922 2008-06-25 2009-05-04 Internal-combustion engine, in particular a two-cylinder engine, provided with a simplified system for variable actuation of the engine valves Active 2030-04-01 US8079331B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08425451.5 2008-06-25
EP08425451 2008-06-25
EP08425451A EP2138680B1 (de) 2008-06-25 2008-06-25 Verbrennungsmotor, insbesondere Zwei-Zylinder-Motor mit einem vereinfachten System zur verstellbaren Betätigung der Motorventile

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US20090320776A1 US20090320776A1 (en) 2009-12-31
US8079331B2 true US8079331B2 (en) 2011-12-20

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US (1) US8079331B2 (de)
EP (1) EP2138680B1 (de)
JP (1) JP5091917B2 (de)
AT (1) ATE483893T1 (de)
DE (1) DE602008002915D1 (de)

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US20130081586A1 (en) * 2011-09-30 2013-04-04 Hyundai Motor Company Variable Valve System
US10961878B2 (en) 2016-04-08 2021-03-30 Mtu Friedrichshafen Gmbh Valve train for the variable actuation of an inlet valve and an outlet valve, and internal combustion engine having a valve train of this type
US11466598B2 (en) * 2019-12-02 2022-10-11 C.R.F. Società Consortile Per Azioni System and method for variable actuation of valves of an internal combustion engine

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EP2397674B1 (de) 2010-06-18 2012-10-24 C.R.F. Società Consortile per Azioni Verbrennungsmotor mit Zylindern, die aktiviert werden können, mit Abgasrückführung durch die variable Steuerung der Aufnahmeventile, und Verfahren zur Steuerung eines Verbrennungsmotors
EP2511489B1 (de) * 2011-04-14 2013-05-29 C.R.F. Società Consortile per Azioni Brennkraftmaschine mit hydro-mechanischem Ventiltriebsystem für das Einlassventil und dessen elektromagnetisches Stellventil
EP2597276B1 (de) 2011-11-24 2014-04-16 C.R.F. Società Consortile per Azioni Brennkraftmaschine mit variablem Ventiltrieb mit einem Drei-Wege-Solenoidventil
EP2653703B1 (de) 2012-04-19 2014-04-30 C.R.F. Società Consortile per Azioni Brennkraftmaschine mit abschaltbaren Zylindern, wobei die deaktivierten Zylinder Abgas in den aktiven Zylindern pumpen; und entsprechendes Steuerverfahren
EP2693007B1 (de) * 2012-07-31 2015-12-09 C.R.F. Società Consortile per Azioni Verbrennungsmotor mit einem System zur variablen Betätigung der Einlassventile mit Dreiwege-Magnetventilen und Verfahren zur Steuerung des Motors
KR101439035B1 (ko) * 2013-06-17 2014-09-05 현대자동차주식회사 차량의 가변 밸브 구동 장치
EP3032054B1 (de) * 2014-12-10 2017-03-29 C.R.F. Società Consortile per Azioni Brennkraftmaschine mit elektronisch gesteuertem hydrauliksystem zur variablen betätigung von einlassventilen, mit einer vorrichtung zum auffüllen des systems mit fluid
DE102016214760B4 (de) 2016-04-28 2018-03-01 Mtu Friedrichshafen Gmbh Verfahren zum Betrieb einer Brennkraftmaschine, Einrichtung zum Steuern und/oder Regeln einer Brennkraftmaschine, Einspritzsystem und Brennkraftmaschine
DE102016219297B4 (de) * 2016-10-05 2021-12-30 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102018129287A1 (de) * 2018-11-21 2020-05-28 Schaeffler Technologies AG & Co. KG Verbrennungsmotor mit hydraulisch variablem Gaswechselventiltrieb

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EP2138680A1 (de) 2009-12-30
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